EP1936190B1 - Compresseur a cylindree variable - Google Patents

Compresseur a cylindree variable Download PDF

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Publication number
EP1936190B1
EP1936190B1 EP06811616A EP06811616A EP1936190B1 EP 1936190 B1 EP1936190 B1 EP 1936190B1 EP 06811616 A EP06811616 A EP 06811616A EP 06811616 A EP06811616 A EP 06811616A EP 1936190 B1 EP1936190 B1 EP 1936190B1
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EP
European Patent Office
Prior art keywords
arms
inclination angle
swash plate
pair
link member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP06811616A
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German (de)
English (en)
Japanese (ja)
Other versions
EP1936190A4 (fr
EP1936190A1 (fr
Inventor
Yuichi Hirabayashi
Keigo Usui
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Marelli Corp
Original Assignee
Calsonic Kansei Corp
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Publication date
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Publication of EP1936190A1 publication Critical patent/EP1936190A1/fr
Publication of EP1936190A4 publication Critical patent/EP1936190A4/fr
Application granted granted Critical
Publication of EP1936190B1 publication Critical patent/EP1936190B1/fr
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms

Definitions

  • the present invention relates to a variable capacity compressor.
  • a conventional variable capacity compressor includes a drive shaft, a rotor fixed to the drive shaft to rotate integrally with the drive shaft, a swash plate which is tiltably attached to the drive shaft, and a link mechanism provided between the rotor and the swash plate (see, for example, Japanese Patent Application Laid-Open Publication No. 10-176658 ).
  • the link mechanism permits the inclination angle of the swash plate to change while transferring torque from the rotor to the swash plate.
  • strokes of pistons are changed so that discharge rate of the compressor is changed.
  • Fig. 17 is a view of a link mechanism disclosed in Publication No. 10-176658 .
  • the link mechanism in Fig. 17 includes a pair of rotor arms 145, 146 which extend from a rotor 140 toward a swash plate 141 and face to each other, a single swash plate arm 147 which extends from the swash plate 141 toward the rotor 140, and a pair of link arms 142A, 142B. These five arms 145, 142A, 147, 142B, and 146 are stacked in the torque transfer direction so that rotation of the rotor 140 is transferred to the swash plate 141.
  • Each of he link arms 142A, 142H has a first end which is linked to the rotor arms 145, 146 by a first linking pin 143 and a second end which is linked to the swash plate arm 147 by a second linking pin 144.
  • the link arms 142A, 142H are rotatable about the first linking pin 143 with respect to the rotor arms 145, 146, and the swash arm 147 is rotatable about the second linking pin 144 with respect to the link arms 142A, 142B, so that the inclination angle of the swash plate 141 with respect to a drive shaft (not shown) is changeable.
  • contact surfaces between the rotor arm 145 and the link arm 142A and contact surfaces between the link arm 142A and the swash plate arm 147 function as torque transferring surfaces and also as rotary sliding surfaces.
  • the rotor arm 145 and the link arm 142A rotationally slide with respect to one another under a large pressure of the torque.
  • the link arm 142A and the swash plate arm 147 also rotationally slide with respect to one another under a large pressure of the torque Ft.
  • the swash plate 141 When the compressor is operative (When the drive shaft rotates), the swash plate 141 receives a large compression reaction force Fp from the pistons that are connected to the swash plate 141. As shown in Fig. 17 (also see Fig. 6 ), since the compression reaction force Fp is applied to the positions anterior to the link mechanism in the rotating direction, the swash plate 141 leans in a direction different from its inclination direction guided by the link mechanism, so that torsion load is given to the swash plate arms 147 in the Y direction in the figure. Accordingly, the link 142 is pressed against the swash plate 141 at two points (C, C) to become wedged and this causes a further increased sliding friction.
  • the above problem can occur in a variable capacity compressor in that a swash plate is attached to a drive shaft via a sleeve and also in a no-sleeve type variable capacity compressor in that a swash plate is directly attached to a drive shaft.
  • An object of the present invention is to provide a no-sleeve type variable capacity compressor capable of preventing an increased sliding friction caused by torsion load.
  • An aspect of the present invention is to provide a variable capacity compressor.
  • the variable capacity compressor includes: a drive shaft; a rotating member fixed to the drive shaft and configured to rotate integrally with the drive shaft; a tilting member having a tilting guide hole formed with a pair of opposite tilting guide faces and tiltably attached to the drive shaft; a link mechanism configured to transfer a rotary torque of the rotating member to the tilting member as allowing the tilting member to tilt; and a piston configured to reciprocate in response to rotation of the tilting member.
  • the link mechanism includes: a pair of opposite arms extending from the rotating member toward the tilting member; a pair of opposite arms extending from the tilting member toward the rotating member; a link member having a first end that is inserted between the arms of the rotating member and a second end that is inserted between the arms of the tilting member, a first linking pin pivotally connecting the first end of the link member and the arms of the rotating member; and a second linking pin pivotally connecting the second end of the link member and the arms of the tilting member.
  • Each of a first maximum inclination angle and a second maximum inclination angle is larger than a fifth maximum inclination angle
  • the fifth maximum inclination angle is larger than a sum of a third maximum inclination angle and a fourth maximum inclination angle.
  • the first maximum inclination angle is a maximum angle of the first end of the link member between the pair of the arms of the rotating member in pre-assembled condition
  • the second maximum inclination angle is a maximum angle of the second end of the link member between the pair of the arm of the tilting member in pre-assembled condition
  • the third maximum inclination angle is a maximum angle of the first linking pin in a bearing clearance in a bearing hole for the first linking pin in pre-assembled condition
  • the fourth maximum inclination angle is a maximum angle of the second linking pin in a bearing clearance in a bearing hole for the second linking pin in pre-assembled condition
  • the fifth maximum inclination angle is a maximum angle of the drive shaft between the pair of the opposite tilting guide surfaces in pre-assembled condition.
  • the first linking pin leans to and contacts with an inner face of the bearing hole at two points and the second linking pin leans to and contacts with an inner face of the bearing hole at two points, so as to receive the compression reaction force that applied to the swash plate.
  • the link member is not pressed against the pair of the arms of the rotating member at two points and against the pair of the arms of the tilting member at two points so as not to be in a wedged state. This prevents such a wedged state causing an increased sliding friction, so that the controllability of the compressor is improved.
  • the first linking pin contacts with two points on the inner face of the bearing hole and the second linking pin contacts with two points on the inner faces of the bearing hole, and also a flexure is caused in at least one of the members constituting the link mechanism (at least one of the pair of arms of the rotating member, the pair of arms of the tilting member, the link member, the first linking pin, and the second linking pin), so that the degree of the inclination of the tilting member further increases.
  • the compression reaction force can be supportively received in the tilting guide hole since the drive shaft contacts with two points on the pair of tilting guide faces in the tilting guide hole before the link member contacts with two points on the pair of arms of the tilting member and the pair of the arms of the rotating member.
  • the link member is thus prevented from contacting with the pair of arms at two points even when an excessive compression reaction force, which is greater than a predetermined value, is applied. This prevents the link member from becoming wedged, so that the high controllability of the compressor is maintained.
  • variable capacity compressor of an embodiment of the present invention will be described with reference to the accompanying drawings.
  • Fig. 1 is a cross-sectional view of the entire variable capacity compressor
  • Fig. 2 shows an inclination of a swash plate in a full stroke condition
  • Fig. 3 shows an inclination of the swash plate in a no-stroke condition.
  • the variable capacity compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 ( Fig.2 ) placed evenly spaced apart in a circumferential direction, a front housing 4 attached to a front end of the cylinder block 2 and having a crank chamber 5 therein, and a rear housing 6 attached to a rear end of the cylinder block 2 via a valve plate 9 and having a suction chamber 7 and a discharge chamber 8 therein.
  • the cylinder block 2, the front housing 4, and the rear housing 6 are fixedly connected to one another by a plurality of bolts 13 so as to make up a housing of the compressor.
  • the valve plate 9 is formed with suction ports (not shown) that communicate the cylinder bores 3 with the suction chamber 7, and discharge ports 12 that communicate the cylinder bore 3 with the discharge chamber 8.
  • a valve system (not shown) adapted to open or close the suction ports is provided on the valve plate 9 at the cylinder block side.
  • a valve system (not shown) adapted to open or close the discharge ports 12 is provided on the valve plate 9 at the rear housing side.
  • a gasket is interposed between the valve plate 9 and the rear housing 6 to maintain airtightness between the suction chamber 7 and the discharge chamber 8.
  • a drive shaft 10 is rotatably supported by radial bearings 17, 18 in support holes 19, 20 that are formed at the center portions of the cylinder block 2 and the front housing 4, respectively. With this structure, the drive shaft 10 is rotatable in the crank chamber 5.
  • the crank chamber 5 accommodates a rotor 21 acting as a "rotating member” fixed to the drive shaft 10, and a swash plate 24 acting as a “tilting member” tiltably and axially slidably attached to the drive shaft 10.
  • the swash plate 24 includes a hub 25 attached to the drive shaft 10, and a swash plate body 26 fixed to a boss segment 25a of the hub 25.
  • Each of the pistons 29 is slidably contained in the cylinder bore 3 and engaged with the swash plate 24 via a pair of hemispherical-shaped shoes 30, 30.
  • a link mechanism 40 is provided between the rotor 21 as the rotating member and the hub 25 of the swash plate 24 as the tilting member.
  • the link mechanism 40 transfers rotary torque from the rotor 21 to the swash plate 24 as allowing changes in the inclination angle of the swash plate 24.
  • the link mechanism 40 will be described in detail later.
  • the inclination angle of the swash plate 24 reduces when the swash plate 24 moves toward the cylinder block 2 (see Fig. 3 ). On the other hand, the inclination angle of the swash plate 24 increases when the swash plate 24 moves away from the cylinder block 2 (see Fig. 2 ).
  • variable capacity compressor is provided with a pressure control mechanism.
  • the pressure control mechanism controls pressure difference (pressure balancing) between the crank chamber pressure Pc in back of the piston 29 and the suction chamber pressure Ps in front of the piston 29 so as to change the inclination angle of the swash plate 24 to change the piston strokes.
  • the pressure control mechanism includes an extraction passage (not shown) that connects the crank chamber 5 with the suction chamber 7 to communicate one another, a supply passage (not shown) that connects the crank chamber 5 with the discharge chamber 8 to communicate one another, and a control valve 33 that is provided in the midstream of the supply passage to open and close the supply passage.
  • FIGS. 4(a) and 4(b) are cross sectional views showing a relation between the drive shaft and tilting guide faces of the swash plate, wherein Fig. 4(a) shows the swash plate in a maximum inclination angle position, and Fig. 4(b) shows the swash plate in a minimum inclination angle position.
  • Figs. 5(a), 5(b), and 5(c) are views of the hub of the swash plate, wherein Fig. 5(a) is a plane view of the hub, Fig.
  • FIG. 5(b) is a sectional view of the hub along a line V-V in Fig. 5(a)
  • Fig. 5(c) is a perspective view of the hub having a cross section along a line V-V in Fig. 5(a) .
  • the swash plate 24 is attached to the drive shaft 10 such that the drive shaft 10 extends through the tilting guide hole 35.
  • the tilting guide hole 35 is formed with a front opening 35a and a rear opening 35b on the both sides of a constricted portion 35c that has a minimum diameter.
  • Each of the front opening 35a and the rear opening 35b is formed in an oval cross sectional shape.
  • the major axes of the front opening 35a and the rear opening 35 are gradually lengthened out from the constricted portion 35c toward the respective opening ends thereof.
  • an inner face of the tilting guide hole 35 includes a pair of tilting guide faces 37 and 37 that are opposed one another. Along the tilting guide faces 37 and 37, the swash plate 24 tilts with respect to the drive shaft 10 (see Figs. 4(a) and 4(b) ).
  • Fig. 6 is a diagrammatic perspective view of an assembly of the driving shaft, the swash plate, and a rotor that are assembled via a link mechanism.
  • Fig. 7 is a cross sectional view of the link mechanism along the line VII-VII in Fig. 2 .
  • the link mechanism 40 includes a pair of arms 41 and 41 which extend from the rotor 21 toward the swash plate 24 and are opposed each other across a slit 41 s, a pair of arms 43 and 43 which extend from the swash plate 24 toward the rotor 21 and are opposed each other across a slit 43s, and a link member 45 inserted in the slit 41s s of the rotor 21 (that is, a slit between the pair of arms 41, 41) and in the slit 43s of the swash plate 43s (that is, a slit between the pair of arms 43, 43).
  • the pairs of arms 41, 41, 43, 43 are respectively arranged to opposite each other in a direction perpendicular to the drive shaft 10, that is, a rotation direction or a rotating torque transferring direction.
  • One end 45a of the link member 45 is rotatably connected to the pair of arms 41, 41 of the rotor 21 by a first coupling pin 46 which extends perpendicular to the drive shaft 10.
  • the other end 45b of the link member 45 is rotatably connected to the pair of arms 43, 43 of the swash plate 24 by a second coupling pin 47 which extends perpendicular to the drive shaft.
  • each of the pair of arms 41, 41 of the rotor 21 is formed with a first bearing hole 41 a witch is configured to rotatably support the first coupling pin 46, and the one end 45a of the link member 45 is formed with a stationary hole 45c to which the first coupling pin 46 is press fitted to be fixed with the arms 41, 41.
  • the pair of arms 43, 43 of the swash plate 24 is formed with a second bearing hole 43a witch is configured to rotatably support the second coupling pin 47, and the other end 45b of the link member 45 is formed with a stationary hole 45d to which the second coupling pin 47 is press fitted to be fixed with the arms 43, 43.
  • the first coupling pin 46 and the second coupling pin 47 are made to have the same length and the same diameter.
  • the width d3 of the slit 41s of the rotor 21, that is, the distance between the pair of the arms 41, 41 of the rotor 21, and the width d4 of the silt 43s of the swash plate 24, that is, the distance between the pair of arms 43, 43 of the swash plate 24 are the same length.
  • the link member 45 is formed in a rectangular shape and its outside faces are formed entirely flat without any steps. With this structure, the width d1 of the one end 45a of the link member and the width d2 of the other end 45b of the link member are the same.
  • Fig. 8 is an explanatory view showing a maximum inclination angle ⁇ 1 of a first end of the link member in the clearance between the pair of arms of the rotor;
  • Fig. 9 is an explanatory view showing a maximum inclination angle ⁇ 2 of a second end of the link member in the clearance between the pair of arms of the swash plate;
  • Fig. 10 is an explanatory view showing a maximum inclination angle ⁇ 3 of the first linking pin in the bearing clearance in the bearing hole for the first linking pin;
  • Fig. 11 is an explanatory view showing a maximum inclination angle ⁇ 4 of the second linking pin in the bearing clearance in the bearing hole for the second linking pin;
  • FIG. 12 is an explanatory view showing a maximum inclination angle ⁇ 5 of the second linking pin in the bearing clearance in the bearing hole for the second linking pin;
  • Fig. 13 is a cross sectional view of the link mechanism in a normal operation; and
  • Fig. 14 is a cross sectional view of the link mechanism under an excessive compression reaction force.
  • the angles ⁇ 1 to ⁇ 5 and the width d1 to d10 are overly depicted for easy-to-understand explanation of the relations of the angles ⁇ 1 to ⁇ 5.
  • a degree of the maximum inclination angle of the link member 45 is determined, as the first maximum inclination angle ⁇ 1, by the clearance (d3-d1 between the slit 41s of the rotor 21 and the one end 45a of the link member 45 ( Fig. 8 ); a degree of maximum inclination angle of the link member 45 is determined, as the second maximum inclination angle ⁇ 2, by the clearance (d4-d2) between the slit 43s of the swash plate 24 and the other end 45b of the link member 45 ( Fig.
  • a degree of the maximum inclination angle of the first linking pin 46 is determined, as the third maximum inclination angle ⁇ 3, by the clearance (d6-d5) between the first linking pin 46 and the first bearing hole 41 a ( Fig. 10 );
  • a degree of the maximum inclination angle of the second linking pin 47 is determined, as the fourth maximum inclination angle ⁇ 4, by the clearance (d8-d7) between the second linking pin 47 and the second bearing hole 43a ( Fig. 11 );
  • a degree of the maximum inclination angle of the swash plate 24 with respect to the drive shaft 10 is determined, as the fifth maximum inclination angle ⁇ 5, by the clearance (d10-d9) between the drive shaft 10 and the pair of the tilting guide faces 37, 37 ( Fig.
  • the fifth maximum inclination angle ⁇ 5 is greater than the sum of the third maximum inclination angle ⁇ 3 and fourth maximum inclination angle ⁇ 4.
  • the first maximum inclination angle ⁇ 1 and the second maximum inclination angle ⁇ 2 are greater than the fifth maximum inclination angle ⁇ 5 (See Figs. 13 and 14 ). Those relations can be described as ( ⁇ 3+ ⁇ 4) ⁇ 5 ⁇ 1, ⁇ 2.
  • relations ⁇ 3 ⁇ 1 and ⁇ 4 ⁇ 2 are established, and accordingly, the following relation is established when the link mechanism 40 is assembled.
  • the first maximum inclination angle ⁇ 1 and second maximum inclination angle ⁇ 2 have a relation as described below.
  • the link member 45 rotates about an end C1
  • the link member 45 stops at an angle corresponding to the maximum inclination angle ( ⁇ 3) of the first linking pin 46 that is allowed by the clearance (d6-d5) between the first linking pin 46 and the first bearing hole 41a. If the link member 45 rotated though the stop point to a point C2, a rotation angle of the link member 45 would be the first maximum inclination angle ⁇ 1.
  • a rotation angle of the link member 45 would be the first maximum inclination angle ⁇ 1.
  • a compression reaction force Fp is applied to the swash plate 24as shown in Figs. 6 and 13 and the swash plate 24 is leaned in a direction different from its inclination movement guided by the link mechanism 40, and then the linking pins 46, 47 is pressed against the inner faces of the bearing hole 41a, 43a and receives the compression reaction force Fp as shown in Fig. 13 .
  • the link member 45 is thus not pressed against the pair of arms 41, 41 at two points and against the pair of arms 43, 43 at two points so as not to be in a wedged state, unlike the conventional structure (Patent Document 1, for example).
  • the swash plate 24 can further be tilted with respect to the drive shaft 10.
  • the linking pins 46, 47 which have smallest cross-sectional area among the linking pins 46, 47, arms 41, arms 43, and link member 45, are mainly deformed.
  • link member 45 does not contact with two points between the pair of arms 43, 43 of the swash plate 24 and with two point between the pair of arms 41, 41 of the rotor 21 due to the relation of ⁇ 3+ ⁇ 4 ⁇ 5 ⁇ 1, ⁇ 2.
  • the drive shaft 10 contacts with two points (points C9 and C10 in the figures) on the pair of tilting guide faces 37, 37 when an excessive compression reaction force generated.
  • the compression reaction force is thus supportively received in the tilting guide hole 35.
  • the link member 45 does not contact with two points between the between the pair of arms 43, 43 of the swash plate 24 and with two point between the pair of arms 41, 41 of the rotor 21 even when an excessive compression reaction force is applied. This prevents an increased sliding friction caused by a wedged state of the link member 45, so that the controllability of the compressor is maintained.
  • Figs. 15 and 16 show examples compared with the present embodiment.
  • the comparative example 1 of Fig. 15 has a structure, in which a relation of ⁇ 1, ⁇ 2 ⁇ 3, ⁇ 4, ⁇ 5 is established.
  • the one end 45a of the link member 45 contacts with two points (points C1 and C2 in the figures) between the pair of arms 41, 41 of the rotor 21 and the other end 45b of the link member 45 contacts with two points (points C3 and C4 in the figures) between the pair of arms 43, 43 of the swash plate 24.
  • the link member 45 can become wedged and the controllability describe in the present embodiment cannot be attained, according to the structure of the comparative example 1.
  • the comparative example 2 of Fig. 16 has a structure, in which a relation of ⁇ 5 ⁇ 1, ⁇ 2, ( ⁇ 3+ ⁇ 4) is established.
  • the drive shaft 10 contacts with two points (points C9 and C10 in Fig. 16 ) of the pair of the tilting guide faces 37, 37 and these two points receives all the compression reaction force Fp.
  • a great degree of sliding friction is thus applied between the tilting guide faces 37, 37 and the drive shaft 10 when the swash plate 24 is tilted and the controllability describe in the present embodiment cannot be attained.
  • the comparative example 2 has a better controllability compared to the comparative example 1 since the contact faces of the drive shaft 10 and tilting guide faces 37, 37 do not fanction as rotary torque transferring surfaces.
  • the link member 35 which largely contributes to the torque transfer, does not be in a wedged state, so that the controllability of the compressor is improved.
  • the drive shaft 10 contacts with two points (C9 and C10) of the pair of tilting guide faces 37, 37 of the tilting guide hole 35, but the link member 45 does not contact with two points between the pair of arms 43, 43 of the swash plate 24 and the pair of arms 41, 41 of the rotor 21.
  • the compression reaction force can be supportively received in the tilting guide hole 35. An increased sliding friction caused by the wedged state of the link member 45 can be prevented and the controllability of the compressor is maintained, even when an excessive compression reaction force is applied.
  • the width d3 of the slit 41s between the arms 41, 41 of the rotor and the width d4 of the slit 43s between the arms 43, 43 of the swash plate are made the same.
  • the link member 45 can be formed in a simple rectangular shape. The manufacturing cost of the link member 45 is substantially reduced since complicated cutting works and the like are not required to manufacture the link member 45.
  • an extrusion molding method and the like can be employed, for example.
  • the first linking pin 46 and second linking pin 47 have the same diameter and length.
  • the manufacturing cost of the link mechanism 40 is substantially reduced since the same pin can be used for both the first linking pin 46 and second linking pin 47.
  • a die for manufacturing the first linking pin 46 and a die for manufacturing the second linking pin 47 can be shared and the number of required dies is reduced.
  • the first linking pins 46 and second linking pins 47 do not have to be prepared separately on a working table and this will reduce burden of assembly workers.
  • the present invention is not limited to the embodiment described above.
  • the holes 41 a, 41 a provided in the rotor arms 41, 41 are bearing holes for pivotally supporting the first linking pin 46 and the hole 45c provided in the link member 45 is a fixing hole for fixing the first linking pin 46 therein.
  • the holes 41a, 41a in the rotor arms 41, 41 can serve as fixing holes for fixing the first linking pin 46 by press fitting and the hole 45c in the link member 45 can serve as a bearing hole for pivotally supporting the first linking pin 46, for example.
  • the linking pins are fixed to the fixing holes by press fitting in the above embodiment; however, in the present invention, the linking pins can be fixed to the fixing holes by screws and the like.
  • the first linking pin can be integrally formed with the link member or the second linking pin can be integrally formed with the link member.
  • the holes 43a, 43a provided in the swash plate arms 43,43 are bearing holes for pivotally supporting the second linking pin 47 and the hole 45c provided in the link member 45 is a fixing hole for fixing the second linking pin 47 by press fitting therein.
  • the holes 43a, 43a in the swash plate arms 43, 43 can serve as fixing holes for fixing the second linking pin 47 by press fitting and the hole 45c in the link member 45 can serve as a bearing hole for pivotally supporting the second linking pin 47.
  • the width d1 of the slit 41s (the slit between the pair of arms 41, 41) of the rotor 21 and the width d2 of the slit 43s (the slit between the pair of arms 43, 43) of the swash plate 24 are formed the same and the link member 45 is formed in a rectangular shape.
  • the width d1 of the slit 41s (between the pair of arms) of the rotor and the width d2 of the slit 43s (between the pair of arms) of the swash plate can differ or the width d1 of the one end 45a of the link member and the width d2 of the other end 45b of the link member can differ.
  • the swash plate 24 is formed by combining the swash plate body 26 and the hub 25, which are separately provided.
  • a swash plate 24, which is previously formed as a single-piece, can be employed, for example.
  • a rotary swash plate is used; however, the present invention can employ a wobble plate (irrotational swash plate).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un compresseur à cylindrée variable satisfaisant à l'expression (θ3 + θ4) > θ5 > θ1, θ2, où θ1 est un premier angle d'inclinaison maximale suivant lequel un organe de liaison (45) est incliné du fait du débattement entre une fente (41s) d'un rotor (21) et une extrémité (45a) de l'organe de liaison (45), θ2 est un deuxième angle d'inclinaison maximale suivant lequel l'organe de liaison (45) est incliné du fait du débattement entre une fente (43s) d'un plateau oscillant (24) et l'autre extrémité (45b) de l'organe de liaison (45), θ3 est un troisième angle d'inclinaison maximale suivant lequel une première broche de connexion (46) est inclinée du fait du débattement entre la première broche de connexion (46) et un premier trou de palier (41a), θ4 est un quatrième angle d'inclinaison maximale suivant lequel une deuxième broche de connexion (47) est inclinée du fait du débattement entre une deuxième broche de connexion (47) et un deuxième trou de palier (43a), et θ5 est un cinquième angle d'inclinaison maximale suivant lequel le plateau oscillant (24) est incliné par rapport à un arbre d'entraînement (10) du fait du débattement entre l'arbre d'entraînement (10) et une paire de surfaces de guidage inclinables (37, 37).

Claims (1)

  1. Compresseur à capacité variable comprenant :
    un arbre d'entraînement (10) ;
    un élément rotatif (21) fixé à l'arbre d'entraînement (10) et conçu pour être solidaire en rotation de celui-ci ;
    un élément oscillant (24) qui présente un trou de guidage d'oscillation (35) pourvu de deux faces de guidage d'oscillation (37, 37) opposées, et qui est fixé à l'arbre d'entraînement (10) de manière à pouvoir osciller ;
    un mécanisme d'articulation (40) conçu pour transférer un couple de rotation de l'élément rotatif (21) à l'élément oscillant (24) en permettant à celui-ci d'osciller, et
    un piston (29) conçu pour décrire un mouvement alternatif en réaction à la rotation de l'élément oscillant (24), étant précisé que le mécanisme d'articulation (40) comprend
    deux bras opposés (41, 41) qui s'étendent à partir de l'élément rotatif (21) en direction de l'élément oscillant (24) ;
    deux bras opposés (43, 43) qui s'étendent à partir de l'élément oscillant (24) en direction de l'élément de rotation (21) ;
    un élément d'articulation (45) qui présente une première extrémité (45a) intercalée entre les bras (41, 41) de l'élément rotatif (21), et une seconde extrémité (45b) intercalée entre les bras (43, 43) de l'élément oscillant (24),
    une première tige d'articulation (46) qui relie de manière pivotante la première extrémité (45a) de l'élément d'articulation (45) et les bras (41, 41) de l'élément rotatif (21) ; et
    une seconde tige d'articulation (47) qui relie de manière pivotante la seconde extrémité (45b) de l'élément d'articulation (45) et les bras (43, 43) de l'élément oscillant (24),
    CARACTERISE EN CE QUE, si on suppose qu'un premier angle d'inclinaison maximal (θ1) est un angle maximal de la première extrémité (45a) de l'élément d'articulation (45) entre les deux bras (41, 41) de l'élément rotatif (21) dans un état pré-assemblé, qu'un deuxième angle d'inclinaison maximal (θ2) est un angle maximal de la seconde extrémité (45b) de l'élément d'articulation (45) entre les deux bras (43, 43) de l'élément oscillant (24) dans un état pré-assemblé, qu'un troisième angle d'inclinaison maximal (θ3) est un angle maximal de la première tige d'articulation (46) dans espace de coussinet dans un trou de coussinet pour la première tige d'articulation (46) dans un état pré-assemblé, qu'un quatrième angle d'inclinaison maximal (θ4) est un angle maximal de la seconde tige d'articulation (47) dans un espace de coussinet dans un trou de coussinet pour ladite seconde tige d'articulation (47) dans un état pré-assemblé, et qu'un cinquième angle d'inclinaison maximal (θ5) est un angle maximal de l'arbre d'entraînement (10) entre les deux surfaces de guidage d'oscillation opposées (37, 37) dans un état pré-assemblé,
    le premier angle d'inclinaison maximal (θ1) et le deuxième angle d'inclinaison maximal (θ2) sont chacun supérieurs au cinquième angle d'inclinaison maximal (θ5), et le cinquième angle d'inclinaison maximal (θ5) est supérieur à une somme du troisième angle d'inclinaison maximal (θ3) et du quatrième angle d'inclinaison maximal (θ4).
EP06811616A 2005-10-12 2006-10-11 Compresseur a cylindree variable Expired - Fee Related EP1936190B1 (fr)

Applications Claiming Priority (2)

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JP2005298093A JP4751166B2 (ja) 2005-10-12 2005-10-12 可変容量圧縮機
PCT/JP2006/320309 WO2007043574A1 (fr) 2005-10-12 2006-10-11 Compresseur a cylindree variable

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EP1936190A1 EP1936190A1 (fr) 2008-06-25
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EP1936190B1 true EP1936190B1 (fr) 2012-04-04

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JP6063150B2 (ja) * 2012-05-28 2017-01-18 サンデンホールディングス株式会社 可変容量圧縮機
JP6047306B2 (ja) * 2012-05-28 2016-12-21 サンデンホールディングス株式会社 可変容量圧縮機
JP6047307B2 (ja) * 2012-05-28 2016-12-21 サンデンホールディングス株式会社 可変容量圧縮機
JP6079379B2 (ja) * 2013-03-29 2017-02-15 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP6171875B2 (ja) 2013-11-13 2017-08-02 株式会社豊田自動織機 可変容量型斜板式圧縮機
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US9802617B1 (en) 2016-05-12 2017-10-31 Nissan North America, Inc. Vehicle accessory power management assembly
ES2895933T3 (es) 2016-07-25 2022-02-23 Caire Inc Compresor de placa oscilante y concentrador de oxígeno que usa el mismo

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JPH10176658A (ja) 1996-12-17 1998-06-30 Zexel Corp 可変揺動板式圧縮機
US6899013B2 (en) * 2003-01-30 2005-05-31 Delphi Technologies, Inc. Hinge for a variable displacement compressor
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US7972118B2 (en) 2011-07-05
JP4751166B2 (ja) 2011-08-17
EP1936190A4 (fr) 2011-02-02
WO2007043574A1 (fr) 2007-04-19
JP2007107438A (ja) 2007-04-26
US20090047145A1 (en) 2009-02-19
EP1936190A1 (fr) 2008-06-25

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